Fluid drive control valve



Fe. 25, w45 c. B. LIVERS FLUID DRIVE CONTROL VALVE Filed Sept. 8, 1941 5 Sheets-Sheet 1 Feb. 26, 1946. c. B. LlvERs FLUID DRIVE CONTROL VALVE Filed sept. a, 1941 5 Sheets-Sheet 2 Feb. 26, 1946. c. B. Llvl-:Rs 2,395,633

` FLUID DRIVE CONTROL VALVE Filled sept. a, 1941 5 sheets-sheet 3- y mw Feb. 26,1946. c. B. LIVERDS FLUID DRIVE CONTROL VALVE Filed Sept. 8. 1941 5 Sheets-Sheet 4 Feb. 26, 1946.

c. B. Livi-:Rs

Filed Sept. 8, 1941 5 Sheets-Sheet 5 i. TMll Patented Feb. Z6, 1946 UNITED STATES PATENT OFFIC rLUfD DR'v'E CONTR-'0L VALVE Carlos Benjamin Livers, San Diege, Calif.

Application VSeptember 8, `1941, SeralNo. 409,956

(on. ca -97) 6 Claims.

This invention relates to a control `for uid drives wherein there is a fiud driven motor or piston in a cylinder operated by fluid pressure.

In uid drives to which the present invention is particularly applicable there is a supply line for 'fluid under .pressure that drives the motor or piston in a cylinder and a return line 'from the moto-r conveying exhaust iluid therefrom which returns the exhaust fluid to aupurmp or the source of supply of fluid pressure. Frequently, the niotor is reversible so that on reverse, the line which originally functioned as a supplyvline functions as the return line and the line which originally .functioned as the return line serves as a supply line.

vAs a means -for controlling the fluid flow `to and from the motor, it is desirable to use a valve lof the pOppet type because of the ability to quickly move the valve from fully closed to fully lopen psition with a minimum amount of throw or actual movement of the valve. Particularly is this true when the uid drive is utilized in connection with gun mounts rwherein one uid drive serves to bring about a traverse of the gun or the turret in which it may be mounted and another uid drive is utilized te bring about the elevation of the gufi.

'The objection to a simple pppet valve in the supply and return lines to and from the motor resides in the 'fact 'that it is very diflicult to so ecnt'rol 'the valve that the motorV will Abe driven at sl'ovv speeds. In other words, when the pop-pet valve is but slightly lifted from its seat a 'considerable volume` of fluid is permitted to pass. Consequentlyy with the use of a simple poppet 'valve the motor usually is caused to run or op'- erate `at a fair degree of speed or else be entirel'y stopped.

A primary object of the 'present invention is to provide an improved valve for controlling fluid flow to and from a fluid operated motor which retains all of the advantages of a poppet type valve and in addition thereto a means for metering the now through the valve when the valve is open, the metering means being automatically operable or brought into operation and functioning independently of the opening between the head of the puppet valve and its seat. In this way the valve may be easily 'and quickly fully 'opened to secure a maximum flow to and from the motor to accomplish speedy operation but When slow operation or ne adjustments are re- 'quired these can also be secured to a much finer degree than that capable of being accomplished by causing the "head oi the 'pppet valve to approac'h its seat.

The ability to nicely 'control small volumes of ovv to vand from the motor is what is commonly called "feel in the hands ofthe operator, it being desirable in most instances to but slightly touch the control handle to produce a positive but nevertheless very slight operation of the fluid driven motor. c

Another object of the invention is to provide a uid drive having a supply line and a return line with control valves 'of the poppet type, each of which is equipped 'with a 'metering means that 'becomes effective on opening 'the valve. With the metering means so arranged that the major 'portion of the metering in the fluid circuit is sometimes accomplished by the metering means inthe supply line and at other times the major portion of the metering is accomplished by the metering means in the return line. B'y proper variation or adjustment of the metering means virtually any desired feel can be secured for controlling small or minor speed operations of the fluid driven motor and consequently of the turret and giuri.

Another object ofthe invention Vis t provide a valve having the abvementi'oned characteristics Which is so designed that a 'ne adjustment of the paris is permissible.

Another bject f the invention is to provide a control valve for a fluid drive wherein the valves controlling the supply line and the return line are operated 01T of a cam shaft common to both valves whereby, upon .rotation of the cam shaft, the supply line valve and the return line valve Will both be opened, the arrangement being such as to secure an automatic balancing of the valves when the structure is in neutral or closed position..

Still another object of the invention is to provide a control for fluid drives having the above characteristics vvhichis so constructed that upon release of the control handles or grips that the valves by reason of their construction will automatically close or return to their neutral position stopping all further fiow that would tend to drive the motor.

`With the foregoing and other objects in view, which will be made manifest in the following detailed description and specifically pointed out in the appended claims, reference is had to the accompanying drawings for an illustrative embodiment of the invention, wherein: Figure .l is a view in -front elevation of a structure embodying the present invention, the pump driven motors being illustrated somewhat diagrammatically;

Fig. 2 is a horizontal section taken substantially upon the line 2 2 upon Fig. 1;

Fig. 3 is a vertical section taken substantially upon the line 3 3 upon Fig. 1;

Fig. 4 is a partial View in vertical section taken substantially upon the line 4 4 upon Fig. 3 in the direction indicated;

Fig. 5 is a horizontal section taken substantially upon the line 5--5 upon Fig. 3 in the direction indicated; f

Fig. 6 is a sectional view through the valve housing and is taken substantially upon the line I--IS upon Fig. 2 in the direction indicated;

Fig. 7 is a sectional View taken substantially upon the line 'I-1 upon Fig. 6; l

Fig. 8 is a sectional view taken substantially upon the line 8 8 upon Fig. 6, it being noted that the line 8 8 upon Fig. 6 is a broken line;

Fig. 9`is a partial view, greatly enlarged, illustrating a typical contour of an inlet valve that supplies fluid to the inlet or supply line that may lead to a fluid driven motor that serves to rotate theA turret or produce a traverse of the gun;

Fig. 10 is a greatly enlarged partial view in vertical section illustrating a typical contour of an outlet valve which controls the outlet in the return line from the motor used. to rotate the turret or produce a traverse of the gun;

Figs. 11 and 12 are views similar to Figs. 9 and 10 illustrating typical contours of valves that may be employed in the fluid circuit that brings about elevation of the gun;

Figs. 13 and 14 are vertical sections through the rock shafts associated With the valves in the two fluid circuits; and y Fig. 15 is a diagram illustrating the rate of flo per degree of valve opening accomplished by ymeans of the Valve embodying the present invention.

Referring to the accompanying drawings wherein similar reference characters designate similar parts throughout, inasmuch asthe present valve has been primarily designed for controlling the uid circuits for hydraulically driven motors employed to elevate guns and to rotate turrets in which the guns may be installed, the present invention will be described in reference thereto although it will be understo-od that the present invention is in no way restricted in its application to use in connection with ordnance but may be generally employed wherever it is desired to have -a fine degree of control over hydraulically driven I'motors at slow speeds.

'.Ifhe device consists of a vmain valve housingv I I! whichmay be equipped at onev corner with a suitable supporting arm or bracket II by which the housing may be suitably mounted 'within Y The column I2 has a cap I'I which when tightened, clamps anti-friction bearings I8 and I9 for a rock shaft 20. On the outer ends of the rock shaft, hand grips 2I and 22 are suitably mounted.

-The ,rock shaft has its center portion between the bearings I'and I9 shaped as illustrated i151 or source of fluid under pressure andthe fiuid K Fig. 3 to accommodate the pin 23 of a hinge 24. A boss is formed on the rock shaft which operates between opposed stops 26 and 2'! limiting rotation of the rock shaft about its horizontal axis. The hand grips 2I and 22 may be rotated about the horizontal axis of the rock shaft 20 or by means of the rock shaft the entire column I2 and bushing I5 can be rotated relatively to the valve housing I0. Normally rotation of the hand grips 2I and 22 about a horizontal axis is intended to control the uid circuit for the fluid driven motor 28 which brings about the elevation of the gun. Rotation of the hand grips 2I and 22 about a vertical axis wherein the column I2 and bushing I5 are also rotated brings about an operation of the motor-29 that rotates the turret or brings about a traverse of the gun. Thus, by a single manipulation of the hand grips the gun may be' elevated or depressed or rotated toward the right or to the left, it being understood that the motors 28 and 29 are reversible. A combination of movements of the hand grips` can be made to cause the gun lto be simultaneously moved in a vertical as well as a rotary direction.

An adjustable link 30 connects the hinge 24 to a ball joint 3I arranged coaxially with the bushing I5. This ball joint in turn is connected by an adjustable link or rod 32 to a clevis 33. By this arrangement rotation of the hand grips 2| and 22 together with the column I2 will not in any way influence the clevis 33 which is operatively connected to the valves which bring about elevation or depression of the gun. Thus, although the hinge24 is not in alignment with bushing I5 rotation of the hinge about the vertical axis of column I2 does not influence clevis 33, the ball of the ball joint merely turning within its socket. Likewise rotation of the hand grips 2l and 22 about a horizontal axis does not influence the position of column I2 and bushing I5 whichl in turn is operatively connectedV to the Avalves of the circuit effecting rotary movement of rotatably supported as by bearings on the bo-ttom of the valve housing. This rock shaft has a downwardly extending bellcrank 4I to whichan arm 42 is connected which in turn is connected by a ball and socket joint 43 to a clamp 44 which is on the bottom of acam shaft 45. No loose connection is necessary between clevis 33 and rock shaft 39 despite the fact' that rotation ofthe rock shaft. 39 will cause the swinging endof arm 38 to travel through an arc. Such arcuate movement is compensated for by the mere bending of the rod 32.

The linkage above described serves to transmit rotary motion-of column I2 and bushing I5 through link'25v and clamp 35 to the cam shaft Pulls or pushes imposed upon link 32by rotating the hand grips 2l and` 22 abouta horizontal axis are translated through arm 33, rock shaft 3S, arm 4 I, links 42 and clamp 44 into rotary motion imparted to the cam shaft 45. TheY cam shafts 31 and 45 each operates its respective pairs of valve sets, one'valve of each valve set being illustrated in Fig. 7 andthe complete valve` set for cam sha/ft 45 being illustrated in Fig. 8. '1n the side of the valve housing'there are formed Atwo openings and 5I. To theopening 5 0 is connected a supply line 52 leading from a pump or other source of fluid under pressure indicated at 53. The opening l is connected by means of a return line 54 to the inlet to the pump. It will be understood that the pump serves to constantly supply fluid to the valve housing under high pressure through line 52 and this iluid that is thus supplied may be utilized in either direction through motors 28 and 2Q. The exhaust or return fluid from the motors is returned through ,the valve housing to the return line 55 and thus returned to the pump.

The opening 55 is branched within the valve housing l5, the branches being indicated at 55 and 56, see Figs. 6, '7, and 8. Within the housing there are four Vhorizontally arranged valve bores 5l, 58, 55, and These valve bores are i' somewhat staggered'with relation to eachother,

valve bores 5l and 59 being slightly offset with respect to the center line of cam shaft 55. Similarly, valve bores 58 and 5! are oppositely offset with respect to the center line or axis of rotation of cam shaft 5l'. The branches 55 and 56 communicate with all of the valve bores 5l, 58, 59, and 59 intermediate their ends. In each valve bore there is disposed a bushing 6l which communicates with the chamber within which its cam shaft 3l or 45 rotates. Within the bushing there is slidably disposed a valve-seat providing member 52 and a tubular puppet valve 53 having a head 55 which has its hollow stem threaded into the top of a piston or valve-seat providing member S2. A valve seat 55 is screwed into the valve housing lll and is held in adjusted position by means of a locknut 65. This valve seat provides a seating surface 5l engageable by the head 5t of the valve. It also provides a shoulder S8 that is adapted to cooperate with an enlargement 69 on the Valve stem to meter the flow of fluid from the branches 55 or 55, as the case may be, outwardly through the valve seat 65. A spring is compressed between bushing Si and packing 1B so as to prevent any leakage from a branch 55 or 55 outwardly through or between the threads on the valve seats 55.

It will be noted that the exposed area on the top of piston or valve-seat providing member is greater than the exposed area on the bottom of bead 55 of the puppet type valve. Consequently, the puppet type valve will be normally urged into closed or seating position as illustrated in Fig. 8.

The poppet type valve having the head 5d constitutes an inlet valve controlling the supply of fluid pressure from the pump to its respective motor 28 or 25. Within bushing El there is slidably disposed an outlet valve ll which may be also regarded as being of the poppet type having a valve head 'l2 adapted to seat upon a valve seat 'i3 provided by the valve-seat providing member 52. The valve-seat providing member 52 also provides a shoulder 'it adjacent which is disposed an enlargement 'l5 formed on the valve. This enlargement is designed to cooperate with the shoulder in metering duid that is returned and which Hows past head l2 when this head is in open position. The valve 'H is bifurcated and equipped with a roller 'IS which roller rests upon the flat top surface of its respective cam shaft as clearly shown in Fig. 7. However, as the valve bores areolset or staggered with relation to their cam shafts, one roller 'l5 will engage the cam shaft 0n one side of its axis while the roller 'EG of the companion valve will engage the top surface of the cam shaft on the opposite side of the axis as illustrated in Fig. 7.

The valves 'H are guided or held against rotation within bushings 6l by means of pins or set screws 'l1 extending inwardly into the bifurcations that house the rollers 15. The tops of the bifurcations extend sufficiently toward the head l2 so that when fluid is being returned through the valve seat 55 and down through the hollow interior 18 of its stem that this fluid, on passing valve head 12, may enter the bifurcations and pass into the valve or bore that houses the cam shaft. From this chamber or Vbore the iluid passes into opening 5| from which it ows back to the pump through return line 513. The valve seats 65 in the four valve bores 5l, 58, 59, and 50 are in turn connected by lines to their respective motors 28 and ES. Thus, the valve seats in the valve bores associated with cam shaft l5 are' connected by lines of tubing lil and 55 to the elevating and depressing motor 23 while the valve seats 65 in the valve bores that are associated with cam shaft 3l are connected by tubing lines 8l and 52 to the traverse motor 25.

lt will be understood that if cam shaft 45 is` rotated that one of its valves 'il will be lifted whereas the other valve 'll will be allowed to drop, this being due to the fact that the rollers 16 are laterally spaced with respect to the axis of rotation of the cam shalt. When valve 'il is lifted it lifts its valve-seat providing member 52 and consequently the poppet type inlet valve having the head 55 which is mounted thereon opening the inlet valve and supplying fluid from a branch to a motor. The companion valve ll will be allowed to descend and disengage its seat i3, thus opening the return line for return ilow from the motor. hus, regardless of which way a cam shaft 3l' or 415 is rotated one of its inlet valves will be opened and the corresponding outlet valve in the adjacent valve bore will also be opened. The direction of rotation of the cam shaft controls the direction of uid supplied to the motor.

Referring now to Figs. 9 to 12, inclusive, it will be noted that the enlar-gement E9 on the inlet poppet valve is cut with a slight degree of taper. A typical taper is 3 as indicated, and the length of the tapered external surface of the enlargement need only be 78/1000" as indicated. The stem of the inlet valve is relieved on both sides of the enlargement as indicated at 83 and 84. When the inlet valve is in seated position as indicated in Fig. 9, the top of the enlargement is directly opposite shoulder 58. Consequently, when the inlet valve is opened so as to disengage the head 64 from its seat 51, the ow to the motor is not governed to any great extent by the amount of opening between the head 513 and the seat 61, but will be governed to a large extent by the degree of opening between the enlargement and shoulder` 68. Thus, as the head 54 is forced open the initial slight opening or space between the head 64 and its seat will govern the volume of flow supplied to the motor. As the inlet valve is forced open further so that there is considerable space between the head 64 and seat 6l, the enlargement 69 comes into play throttling or metering the fluid ilow between its external surface and shoulder S8. Of course, as the valve is lifted due to the taper of the enlargementl this space between the enlargement and shoulder 58 continuously increases supplying greater and greater volumes of ow as the valve is opened. The volume supplied however is not commensurate with the amount of opening between head 64 and seat 61 but is governed by the space between the enlargement 69 and shoulder 68. As

l the enlargement l and its shoulder lll.

the valve approaches its fully open position the bottom of the enlargement 69 entirely clears the shoulder 58 and a greater volume of fluid is permitted to pass. In this Way all of the advantages of a poppet valve are retained in that slight rotation of a rock shaft will accomplish a full opening of the valve for high speed operation of the motor. Slight rotations of the rock shaft which will serve to only partially open the Valve do not bring about a iiow of iiuid that is commensurate with the opening between the valve head 64 and the valve seat 6l, but instead commensurate with the degree of opening between enlargement 69 and shoulder 68.

As illustrated in Fig. 10, the Valve 'il is. similarly constructed, that is the enlargement 'l5 has an external taper which is disposed adjacent the shoulder llt. When the valve head 'l2 leaves its seat 'I3 the volume of ilovv through this outlet valve is not commensurate with the degree of opening between the valve and its seat but is commensurate with the degree of opening between The contours of these valves do not necessarily have to conform closely to that illustrated in Figs. 9 and 10. Ordinarily, the length of the enlargement in the case of valves controlling the iiow of fluid to and from the motor that brings about a traverse of the gun is greater than the lengths of the enlargements on the valves that are in the circuit of the motor that'brings about the elevation and depression of the gun. Typical valves and enlargements used in the elevation circuit are illustrated in Figs. 11 and 12, wherein it will be noted that the effective length of the enlargement is considerably smaller or shorter than the effective lengths of the enlargements in Figs. 9 and l0. It is not necessary either that the taper be a straight-line taper as indicated. The taper may be a convex taper or a concave taper. In some instances a combined convex and concave taper or other configuration may be given the enlargement. The shaping of the contours of the enlargements governs to a great extent the feel of the entire valve control. Thus, if the volume of flow is plotted per degree of valve opening as illustrated in Fig. l5, the volume of uid ow per degree of valve opening will rather suddenly increase as indicated by the dotted line 85 on this gure. If the valve is equipped With the metering enlargements and the volume of flow plotted per degree of valve opening a curve such as that indicated by the line 86 will be obtained wherein it will be noted that a considerable degree of valve opening is obtained before any large volume of fluid fiow is permitted to pass to the motor. As the valve opening continues however the volume permitted to ilow by increases quite rapidly until the valve is fully opened. Consequently, a very fine adjustment or control of the uid circuit to and from the motor is obtainable. It is possible by proper contour arrangements of the valves to secure virtually any desired curve 86. Manifestly at the start of the curve, that is from points 8l' to 88, the shape of the curve is controlled by the head of the valve leaving its seat. From point 82% to point 89 on the curve Vthe major metering` may be performed by the enlargement on the inlet valve. From point 89 to point 9D on the curve the major metering may be performed by the enlargement on the outlet valve in the same circuit. By properly shaping the enlargements 69 and l5, the metering and consequently the shape of the curve 85 can be varied considerably. In other words, first one enlargement in a circuit may come into play to be largely effective in metering the flow, and then another enlargement may come into play or both enlargements may be simultaneously effective to meter the flow supplied to, and returned from the motor.

It will be manifest that in as delicate valve control as the present invention affords, that no play should be left between any of the parts transmitting motion from the Ygrips 2| and 22 to the cam shafts .il and 65. By using pre-loaded bearings, hardened parts, and honing or lapping the fits between the parts, it is possible to have motion transmitted from the grips to the cam shafts 31 and t5 with only about 1/1000 play. When this is secured, the advantages of the metering resulting in the delicate feel or delicate control are readily apparent to those skilled in utilizing iiuid drive control of this character. By having the valve seat -adjustable, a very accurate setting of the construction is possible. Manifestly, the positions of the seating surfaces of the poppet valve heads are governed by the location of thecam shafts, the lengths of the pistons or valve seat providing members, and the lengths of the tubular valves. By having the valve seats 65 adjustable the parts may be easily assembled and the valve seat accurately adjusted with respect to the seating surfaces of its poppet valve head. Thus, no lost motion need be present in the valves themselves. Where the valves are replaced either because of damage or because of a desire for the substitution of a valve to secure an enlargement with a different contour to secure a different feel the adjustable valve seat compensates for any minute inaccuracy inV the'shape of the replacing valve. It is usually desirable to so adjust valve seat 55 that the heads of the inlet valves will be just barely unseated so that even though the cam shafts 31 and l5 are in neutral position a very minute amount of fluid pressure is transmitted to the motor subjecting the motor at all times to the full degree of pressure developed by pump 53 and ready for irnmediate action as soon as the grips are disturbed. As the pressures supplied to the valves associated with each cam shaft are the same and the valves are urged against the cam shafts by the exposed surfaces on the valve-seat providing member 62, the units associated with each rock shaft tend to balance each other through the cam shaft. Thus, any amount of opening between an inlet valve head l and its seat will normally be immediately balanced by an equivalent amount of opening in the companion valve unit. Whenever the grips 2l and 22 are released as the pressure on the pistons or valve-seat providing member 52 has a greater effective area than that eX- posed on the undersides of the heads li the pressure from the pump will serve to automatically seat the inlet valves returning the cam shafts 3'! and l5 to their` neutral positions. The pressure exerted on the cam shafts is sufficient to operate the linkage connecting the cam shafts with the grips so as to likewise return the grips to their neutral positions. Thus, when the grips are released, further operation of the motors 28 and 2Q automatically stops and all parts of the structure instantly return to their original or neutral positions.

It Will be noted from the above-described construction that quite a variety of adjustments are permissible after manufacturing to accommodate the construction to a variety of varying conditions in use, and thus acquire the desired feelJ One adjustment is permissible by adjusting the pin 23 of the hinge 24 to vary the throw of the hinge and consequently of the clevis 33 per given rotary movement of the grips 2l and 22. The valve seat E5 can also be readily adjusted and whenever desired, the valves themselves may be easily replaced to secure enlargements on the valves with varying contours which govern the metering of the fluid supplied to and returned from the motors.

From the above-described construction it will be appreciated that an improved control is provided for fluid drives wherein all of the advantages of a quick opening poppet valve are retained and in addition thereto, an automatic delicate metering of the flow is secured during the initial opening of the valve which is desired in securing ne adjustments or slow speed movements of the turret and of the gun.

Various changes may be made in the details of construction without departing from the spirit or scope of the invention as defined by the appended claims.

Iclaim:

l. A valve structure for a fluid drive wherein there is a fluid pressure source and a reversible fluid pressure operated motor, comprising means for providing a housing having an inlet from the iluid pressure source, a pair of supply conduits leading to opposite sides of the motor, and a return conduit for returning fluid to the source of supply, a tubular poppet type of valve for each of the supply conduits controlling the now of fluid from the inlet thereto and permitting fluid to be returned from the motor therethrough, a return valve for each tubular valve controlling the return flow therethrough, and operating means common to both return valves for alternately causing the return valves to open and close the passages through their tubular valves respectively and when closed to unseat their tubular valves, direct mechanical connections between each return valve and the operating means, the seats for the tubular valves being adjustable toward and away from the operating means to eliminate loose play between the tubular valves, their return valves and the operating means when all of the Valves are in closed position.

2. A valve structure for a fluid drive wherein there is a fluid pressure source and a reversible fluid pressure operated motor, comprising means providing a housing having an inlet from the fluid pressure source, a pair of supply conduits leading to opposite sides of the motor, and a return conduit for returning fluid to the source of supply, a tubular poppet type valve for each of the supply conduits controlling the flow of fluid from the inlet thereto and permitting iluid to be returned from the motor therethrough, a return valve for each tubular valve controlling the return flow therethrough, and operating means common to both return valves for alternately causing the return Valves to open and close the passages through their tubular valves respectively and when closed to unseat their tubular valves, direct mechanical connections between each return valve and the operating means, the seats for the tubular valves being themselves tubular and threaded into the housing and extending to the exterior thereof whereby they may be adjusted toward and away from the operating means to eliminate loose play between the tubular valves, the return valves and the operating means when all of the valves are in closed position.

p3. A valve structure for a uid drive wherein there is a fluid pressure source and a reversible fluid pressure operated motor, comprising means providing a housing having an inlet from the fluid pressure source, a pair of supply conduits leading to opposite sides of the motor and a return conduit for returning fluid to the source of supply, a tubular poppet type valve for each of the supply conduits controlling the flow of fluid from the inlet thereto and permitting fluid to be returned from the motor therethrough, a return valve for each tubular valve controlling the return flow therethrough, and operating means common to both return valves for alternately causing the return valves to open and close the passages through their tubular valves respectively and when closed to unseat their tubular valves, direct mechanical connections between the return valves and the operating means, means on said tubular valves presenting areas subject to inlet pressure which are eiective to urge the valves toward the operating means with equal opposed effect whereby the valve structure will be always urged by fluid pressure into a neutral position wherein al1 valves are closed, the seats for the-tubular valves being adjustable from the exterior of the housing toward and away from the operating means to eliminate loose play between the tubular valves, their return valves and the operating means when all of the valves are in closed positions.

4. A valve structure for fluid drives wherein there is a fluid pressure source and a reversible fluid pressure operated motor comprising means providing a housing having an inlet from the source, supply conduits leading to the opposite sides of the motor and a return conduit for returning fluid to the source, a tubular valve for each supply conduit controlling ow from the inlet thereto and allowing returning uid to pass therethrough to the return conduit, return valves adapted to seat on the tubular valves and control fluid returning therethrough, a rock shaft having a flat side, and a direct mechanical connection operatively connecting the return valves to the dat side of the rock shaft on opposite sides of the axis of rotation of the rock shaft whereby upon rocking the rock shaft the return valves will be caused to alternately open and close their respective tubular valves and when closed to unseat their respective tubular valves, the Valve seats of the tubular valves being adjustable toward and away from the rock shaft whereby loose play between the tubular valves, the return valves and the rock shaft when the valves are all closed may be eliminated.

5. A valve structure for fluid driveswherein there is a fluid pressure source and a reversible uid pressure operated motor comprising means providing a housing having an inlet from the source, supply conduits leading to the opposite sides of the motor and a return conduit for returning iiuid to the source, a tubular valve for each supply conduit controlling flow from the inlet thereto and allowing returning fluid to pass therethrough to the return conduit, return valves adapted to seat on the tubular valves andxcontrol fluid returning therethrough, a rock shaft having a flat side, and a direct mechanical connection operatively connecting the return valves to the flat side of the rock shaft on opposite sides of and equi-distant from the axis of rotation of the rock shaft whereby upon rocking the rock shaft the return valves will be caused to alternately open and close their respective tubular valves and when closed to unseat their respective supply conduits leading to the opposite sides of the motor and a return conduit for returning iluid to the source, a tubular valve for each. supply conduit controlling flow from the inlet thereto and allowing return fluid to pass therethrough to the return conduit, return valves adapted to seat on the tubular valves and control uid returning therethrough, a rock shaft having a flat side, and a direct mechanical connection operatively connecting the return valves to the flat side of the rock shaft on opposite sides of the axis of rotation of the rock shaft whereby upon rocking the rock shaft the return valves will be caused to alternately open and close their respective tubular valves and when closed to unseat their respective tubular valves, the valve seats of the tubular valves being tubular and extending to the exterior of the housing and being adjustable toward and away from the rock shaft whereby loose play between the tubular valves, their return valves and the rock shaft when the valves are all in closed position may be eliminated.

CARLOS BENJAMIN LIVERS. 

